WO2023247817A1 - Coquille de palier, palier, moteur à piston et utilisation d'une coquille de palier - Google Patents

Coquille de palier, palier, moteur à piston et utilisation d'une coquille de palier Download PDF

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Publication number
WO2023247817A1
WO2023247817A1 PCT/FI2022/050449 FI2022050449W WO2023247817A1 WO 2023247817 A1 WO2023247817 A1 WO 2023247817A1 FI 2022050449 W FI2022050449 W FI 2022050449W WO 2023247817 A1 WO2023247817 A1 WO 2023247817A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing shell
bearing
shell
oil groove
circumferential direction
Prior art date
Application number
PCT/FI2022/050449
Other languages
English (en)
Inventor
Pasi Halla-Aho
Luciano PERINEL
Jaakko ISTOLAHTI
Janne Joonas LEPPÄKANGAS
Jukka-Pekka VESALA
Original Assignee
Wärtsilä Finland Oy
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Wärtsilä Finland Oy filed Critical Wärtsilä Finland Oy
Priority to PCT/FI2022/050449 priority Critical patent/WO2023247817A1/fr
Publication of WO2023247817A1 publication Critical patent/WO2023247817A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C9/00—Bearings for crankshafts or connecting-rods; Attachment of connecting-rods
    • F16C9/04—Connecting-rod bearings; Attachments thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
    • F16C17/022—Sliding-contact bearings for exclusively rotary movement for radial load only with a pair of essentially semicircular bearing sleeves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/1045—Details of supply of the liquid to the bearing
    • F16C33/1055—Details of supply of the liquid to the bearing from radial inside, e.g. via a passage through the shaft and/or inner sleeve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
    • F16C33/1065—Grooves on a bearing surface for distributing or collecting the liquid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps
    • F16C2360/22—Internal combustion engines

Definitions

  • the present invention concerns a bearing shell for a bearing that connects a connecting rod of a piston engine to a crankshaft, as defined in claim 1 .
  • the invention also concerns a bearing, a piston engine and a use of a bearing shell.
  • a piston rod connects each piston to a crankshaft.
  • the bearing connecting the piston rod to the crankshaft is often referred to as a big end bearing.
  • crankpin wears. However, the wear is not even. The crankpin wears more at the area that forms a lower part of the crankpin when the piston is at top dead center, as shown in figure 1 . Even the lower part of the crankpin does not wear uniformly, but the area aligned with the oil groove of the bearing experiences less wear than the areas on either side of the oil groove. Due to the uneven wear, a protruding portion, i.e. a ridge can be formed in the middle of the crankpin. The height of the ridge can correspond to the thickness of the oil film. An exaggerated view of such a ridge in shown in the enlarged views of figures 1 and 2.
  • the inner surface of the bearing shell according to the invention is provided with an oil groove, the oil groove comprising a first portion, a second portion and a third, intermediate portion connecting the first portion and the second portion, wherein the first portion and the second portion are straight and run in the circumferential direction of the bearing shell, and wherein the third portion is narrower than the first portion and the second portion and at least part of the third portion runs in a direction that deviates in an axial direction of the bearing shell from the circumferential direction of the bearing shell.
  • the third portion is configured so that on each imaginary line drawn from the first portion to the second portion on the inner surface of the bearing shell in a circumferential direction, there is at least one section that is outside the third portion of the oil groove. There is thus no area on the outer surface of the crankpin that would not come into contact with the inner surface of the bearing shell, which helps keeping the wear of the crankpin more uniform.
  • the third portion is arranged in the circumferential direction in the middle of the bearing shell.
  • At least part of the third portion has a serpentine shape.
  • said bearing shell forms a lower half of the bearing
  • the upper half of the bearing is formed by a bearing shell comprising no oil groove or an oil groove extending only over part of the bearing shell in the circumferential direction.
  • the bearing shell defined above can be used as a lower half of a bearing that connects a connecting rod of a piston engine to a crankshaft.
  • Fig. 1 shows part of a crankshaft and a connecting rod of a piston engine and a prior art bearing shell
  • Fig. 3 shows a prior art bearing shell
  • Fig. 4 shows a perspective view of a bearing shell according to an embodiment of the invention
  • Fig. 5 shows a plan view of the bearing shell of Fig. 1
  • Fig. 6 shows a bearing shell according to another embodiment of the invention
  • Fig. 7 shows a bearing shell according to still another embodiment of the invention.
  • Figure 1 shows part of a crankshaft 5 and a connecting rod 4 of a piston engine.
  • the engine is a large internal combustion engine, such as a main or an auxiliary engine of a ship or an engine that is used at a power plant for producing electricity.
  • the engine has a cylinder bore of at least 150 mm.
  • Each cylinder of the engine is provided with a piston that moves in a reciprocating manner in the cylinder.
  • the engine can have any reasonable number of cylinders.
  • the connecting rod 4 connects the piston to the crankshaft 5 and converts the reciprocating motion of the piston to the rotating motion of the crankshaft 5.
  • FIG. 1 The piston moves between top dead center and bottom dead center.
  • Figure 2 illustrates a situation, where the piston is at bottom dead center.
  • the connecting rod 4 is connected to the crankshaft 5 by means of a bearing 3.
  • the bearing 3 can be referred to as a big end bearing.
  • the bearing 3 is a slide bearing.
  • the bearing 3 is rotationally fixed to the connecting rod 4.
  • the bearing 3 does thus not rotate relative to the connecting rod 4.
  • the bearing 3 has an inner surface, which forms a bearing surface.
  • the bearing surface faces a crankpin 6 of the crankshaft 5 and the bearing 3 can rotate relative to the crankpin 6.
  • Lubricating oil is supplied between the crankpin 6 and the bearing surface of the bearing 3 to form an oil film between the parts.
  • the bearing 3 is formed of two bearing shells 1 , 2.
  • the bearing shells 1 , 2 are semicircular parts.
  • a first, lower bearing shell 1 forms a lower half of the bearing 3 and a second, upper bearing shell 2 forms an upper half of the bearing 3.
  • the expression “upper half’ refers to that half of the bearing 3 that is closer to the upper end of the cylinder, i.e. the top dead center.
  • the expression “lower half’ refers to that half that is farther from the upper end of the cylinder.
  • the longitudinal axis of the cylinder does not need to be aligned with the vertical direction, but e.g. in a V-engine the cylinders can be tilted relative to the vertical direction.
  • the bearing 3 is thus not necessarily divided into the two halves by a horizontal plane.
  • Figures 1 and 2 show a prior art bearing 3.
  • the lower bearing shell 1 is also shown in figure 3.
  • the lower bearing shell 1 of the bearing 3 is provided with an oil groove 10 that is arranged on the inner surface of the bearing shell 1 , i.e. on the bearing surface.
  • the oil groove 10 is straight and extends in the circumferential direction of the bearing shell 1 over the whole bearing shell 1. In the axial direction of the bearing shell 1 , the oil groove 10 is arranged in the middle of the bearing shell 1 .
  • Each end of the oil groove 10 is provided with a plurality of oil holes 14.
  • the upper bearing shell 2 is plain. There is thus no oil groove on the bearing surface of the upper bearing shell 2.
  • crankpin 6 wears. Often the wearing is not uniform, but lower part of the crankpin 6 wears more.
  • the expression “lower part” refers to that side of the crankpin 6 that is located in top dead center position of the piston farther from the top dead center. Nor does the lower part of the crankpin 6 wear uniformly.
  • the part aligned with the oil groove 10 wears less than the rest of the surface of the crankpin 6. Wearing of the crankpin 6 is caused for example by abrasive particles between the bearing surface and the crankpin 6. At the area aligned with the oil groove 10, there is a larger gap between the bearing surface and the crankpin 6, and the abrasive particles do thus not grind the crankpin 6 to the same extent as elsewhere.
  • a protruding area, or a ridge 7 is formed at the area aligned with the oil groove 10.
  • the enlarged views of figures 1 and 2 show an exaggerated view of the ridge 7.
  • the height of the ridge 7 can be similar to the thickness of the oil film on the bearing surface.
  • the ridge 7 comes into contact with the upper bearing shell 2. Because the bearing surface of the upper bearing shell 2 is plain, there is no groove that could accommodate the ridge 7. As a consequence, the bearing 3 is loaded more at the area that is aligned with the ridge 7. The non-uniform loading of the bearing 3 can cause problems. Problems can be encountered in particular after engine overhaul. When the bearing 3 has been replaced by a new bearing with an intact bearing surface, the overloading of the upper bearing shell 2 is even more likely.
  • the problems caused by the non-uniform wear can be reduced by the bearing shell 1 according to the invention.
  • the bearing shell 1 according to the invention can be used as the lower bearing shell of the bearing 3 that connects the connecting rod 4 of a piston engine to a crankshaft 5.
  • the bearing shell 1 according to the invention can thus replace the bearing shell 1 shown in figures 1-3.
  • Figures 4-7 show some embodiments of the bearing shell 1 according to the invention.
  • the inner surface of the bearing shell 1 according to the invention is provided with an oil groove 10.
  • the oil groove 10 comprises a first portion 11 , a second portion 12 and a third, intermediate portion 13 connecting the first portion 11 and the second portion 13.
  • the first, second and third portions 11 , 12, 13 thus form a continuous oil groove 10 onto the bearing surface.
  • the first portion 11 and the second portion 12 are straight and run in the circumferential direction of the bearing shell 1 .
  • the edges of the first portion 11 and the second portion 12 are thus parallel with the circumferential direction of the bearing shell 1.
  • the first and the second portions 11 , 12 are aligned with each other.
  • the first portion 11 and the second portion 12 have the same width with each other.
  • the width of the first portion 11 and the second portion 12 is approximately 20 percent of the width of the bearing shell 1 .
  • the width could be, for instance, in the range of 15-30 percent of the width of the bearing shell 1 .
  • the first portion 11 and the second portion 12 are arranged in the axial direction of the bearing shell 1 , i.e. in the axial direction of the bearing 3, in the middle of the bearing shell 1 .
  • the third portion 13 is narrower than the first portion 11 and the second portion 12, and at least part of the third portion runs 13 in a direction that deviates from the circumferential direction of the bearing shell 1 towards a side of the bearing shell 1 . Because of the narrower groove, larger part of the bearing shell 1 is in contact with the crankpin 6 and the crankpin 6 wears more uniformly. Because the direction of the third portion 13 differs from the circumferential direction, continuous non-contact portions in the circumferential direction of the bearing shell 1 can be reduced. This reduces forming of a ridge at the area of the oil groove 10.
  • the width of the third portion 13 can be, for instance, in the range of 20-60 percent of the width of the first portion 11 and the second portion 12.
  • the third portion 13 is configured so that on each imaginary line drawn from the first portion 1 1 to the second portion 12 on the inner surface of the bearing shell 1 in the circumferential direction, there is at least one section that is outside the third portion 13.
  • Each of said imaginary lines thus comprises a portion that is not part of the oil groove 10 but is located on the bearing surface. There is thus no area on the outer surface of the crankpin 6 that would not come into contact with the inner surface of the bearing shell 1 , which helps keeping the wear of the crankpin 6 more uniform.
  • the third portion 13 extends in the axial direction of the bearing shell 1 from the imaginary extensions of the edges of the first portion
  • the first portion 11 extends in the circumferential direction to a first end of the bearing shell 1 and the second portion 12 extends to a second end of the bearing shell 1 .
  • the oil groove 10 thus extends in the circumferential direction over the whole bearing shell 1 .
  • the oil groove 10 could extend in the circumferential direction of the bearing shell 1 over only part of the bearing shell 1 .
  • the oil groove 10 could extend over an angle of 100-180 degrees. If the oil groove 10 does not extend over the whole bearing shell 1 , the oil groove 10 is preferably arranged in the middle of the bearing shell 1 in the circumferential direction.
  • the third portion 13 extends in the circumferential direction of the bearing shell 1 over an angle of approximately 60 degrees. In a bearing shell 1 , where the oil groove 10 extends over the whole bearing shell 1 , the third portion 13 could extend over an angle of 40-100 degrees. In the embodiments of the figures, the third portion 13 is arranged in the circumferential direction in the middle of the bearing shell 1.
  • the third portion 13 has a serpentine shape.
  • the shape is thus similar to the zigzag shape of figure 5, but instead of straight sub-sections, the third portion 13 comprises curved sub-sections. Even in this embodiment, at least part of the third portion 13 is arranged so that it does not overlap with the imaginary extension of the centerline of the first portion 11 and the second portion 12.
  • first portion 11 and the third portion 13 there could be a transition zone, where the width of the oil groove 10 gradually decreases.
  • a similar transition zone could be arranged between the third portion 13 and the second portion 12.
  • the upper bearing shell 2 can be similar to the prior art bearing shells 2.
  • the upper bearing shell 2 can have a bearing surface that is not provided with any oil groove.
  • the upper bearing shell 2 could be provided with an oil groove extending only over part of the bearing shell 2 in the circumferential direction.
  • the upper bearing shell 2 could be provided at its both ends with an oil groove that is configured to form a continuation for the first and second portions 11 , 12 of the oil groove 10 of the lower bearing shell 1 .

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
  • Sliding-Contact Bearings (AREA)

Abstract

La surface interne de la coquille de palier (1) pour un palier (3) qui relie une tige de liaison (4) d'un moteur à piston à un vilebrequin (5) est dotée d'une rainure d'huile (10), la rainure d'huile (10) comprenant une première partie (11), une deuxième partie (12) et une troisième partie intermédiaire (13) reliant la première partie (11) et la deuxième partie (12). Les première et seconde parties (11, 12) sont droites et s'étendent dans la direction circonférentielle de la coquille de palier (1). La troisième partie (13) est plus étroite que les première et deuxième parties (11, 12), et au moins une partie de la troisième partie (13) s'étend dans une direction qui s'écarte dans une direction axiale de la coquille de palier (1) de la direction circonférentielle de la coquille de palier (1) en direction d'un côté de la coquille de palier (1).
PCT/FI2022/050449 2022-06-22 2022-06-22 Coquille de palier, palier, moteur à piston et utilisation d'une coquille de palier WO2023247817A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/FI2022/050449 WO2023247817A1 (fr) 2022-06-22 2022-06-22 Coquille de palier, palier, moteur à piston et utilisation d'une coquille de palier

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/FI2022/050449 WO2023247817A1 (fr) 2022-06-22 2022-06-22 Coquille de palier, palier, moteur à piston et utilisation d'une coquille de palier

Publications (1)

Publication Number Publication Date
WO2023247817A1 true WO2023247817A1 (fr) 2023-12-28

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PCT/FI2022/050449 WO2023247817A1 (fr) 2022-06-22 2022-06-22 Coquille de palier, palier, moteur à piston et utilisation d'une coquille de palier

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4201176A (en) * 1977-01-04 1980-05-06 Sulzer Brothers Limited Radial bearing for an internal combustion engine
US20140126847A1 (en) * 2011-02-25 2014-05-08 Mahle International Gmbh Bearing arrangement
WO2016157575A1 (fr) * 2015-03-31 2016-10-06 三菱重工業株式会社 Bielle et moteur du type à crosse comportant cette dernière
US20170307005A1 (en) * 2016-04-20 2017-10-26 Ford Global Technologies, Llc Connecting rod for an internal combustion engine
EP3401560A1 (fr) * 2017-05-09 2018-11-14 Volvo Car Corporation Ensemble bielle et vilebrequin

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4201176A (en) * 1977-01-04 1980-05-06 Sulzer Brothers Limited Radial bearing for an internal combustion engine
US20140126847A1 (en) * 2011-02-25 2014-05-08 Mahle International Gmbh Bearing arrangement
WO2016157575A1 (fr) * 2015-03-31 2016-10-06 三菱重工業株式会社 Bielle et moteur du type à crosse comportant cette dernière
US20170307005A1 (en) * 2016-04-20 2017-10-26 Ford Global Technologies, Llc Connecting rod for an internal combustion engine
EP3401560A1 (fr) * 2017-05-09 2018-11-14 Volvo Car Corporation Ensemble bielle et vilebrequin

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